Dry break valve assembly

ABSTRACT

A fluid system component is provided that includes first and second elements configured to be removably engaged with each other and defining a fluid passageway when engaged. The first element defines three grooves, each of which includes a terminal portion. Correspondingly, the second element includes three engagement members each of which is configured and arranged to be received in, and travel along, a corresponding groove. The presence of a predetermined line pressure in the fluid passageway forces each engagement member into the terminal portion of the corresponding groove, so as to substantially foreclose disengagement of the first and second elements until the fluid pressure in the fluid passageway has reached a predetermined magnitude.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a divisional of U.S. patent application Ser. No.10/164,945, filed Jun. 7, 2002, now U.S. Pat. No. 7,152,630 entitledFLUID SYSTEM COUPLING, which is a continuation-in-part of U.S. patentapplication Ser. No. 09/628,075, now U.S. Pat. No. 6,672,327, entitledDRY BREAK VALVE ASSEMBLY, filed Jul. 28, 2000, each of which areincorporated herein in their entirety by this reference.

BACKGROUND

1. Technological Field

The present invention relates generally to fluid system components. Moreparticularly, embodiments of the present invention relate to a fluidsystem component configured to utilize the line pressure of the fluidsystem, wherein the fluid system component is employed, in a way thatsubstantially prevents takedown of the fluid system component until thefluid system line pressure, or relative pressure differential, changesto a safe level.

2. Related Technology

In recent years, environmental concerns have been receivingsignificantly more attention, and various governmental agencies haveresponded by implementing stringent regulations to reduce or preventpollution. Many of these regulations and concerns are directed towardsthose industries that transport fluids. For example, it is verydifficult to transport a fluid without spilling or leaking some of thefluid into the environment. Thus, some environmental regulations requirethat minimal leaking occur during handling, processing, ortransportation of the fluid.

These environmental concerns become especially clear when consideringthe magnitude of the industries that handle hazardous fluids that, ifallowed to escape even in relatively small quantities, can causesignificant damage. There is a concern, therefore, to protect both thepublic and the environment from these types of fluids. While some fluidsthat are transported, such as water and milk, may not pollute theenvironment when they are leaked or spilled, the loss of fluid into theenvironment is nevertheless viewed as a general waste of resources. Moregenerally, the loss of fluid into the environment is not desirable evenif the fluid does not contribute to pollution.

Within the transportation industry, a variety of different devices areused to transport a fluid from a source to a destination. These devicesoften use valve assemblies and conduits of various types to both connectthe source to the destination as well as to manage fluid flow throughthe conduit. Typically, the conduit is pressurized to direct fluidtoward the desired destination. With each transfer of fluid, there is arisk that leakage will occur due to human error, equipment malfunctions,or the like.

A common source of fluid leaks and fluid spills are the valves and othercomponents and devices employed in fluid systems. By way of example,some valves may have leaks that permit flow through the valve even whenthe valve is secured in the closed position. In other instances, one ormore joints defined by constituent elements of the valve, such as in thecase of valves designed to be taken down in two or more pieces, and/orone or more joints at least partially defined by the valve, such as avalve-to-flange connection, may be defective, resulting in leakage ofsome or all of the system fluid. Unfortunately, problems such as theseoften do not manifest themselves until after flow has been establishedthrough the valve, component, or device.

Thus, in many instances, the system operator is limited in terms of theaffirmative steps that can be taken to prevent a spill that may resultfrom one or more defective joints, and oftentimes can only correct thespill when it occurs. This is true in the case of joints that aredefectively assembled, or are otherwise defective upon assembly, as wellas in the case of joints that become defective over a period of time dueto operating, or other, conditions.

Other problems exist as well. For example, various types of valves havebeen designed to stop, or “check,” fluid flow through the valve when thevalve is taken down into two or more constituent parts or assemblies.One known device for checking fluid flow is a ball check valve. A ballcheck valve is essentially a ball which rests against a ball seat toform a valve. An operator may use the ball check valve to initiate orterminate the fluid flow. Despite the check feature of the ball checkvalve, a problem exists in the integrity of the fluid transfer systemwhen the valve or conduit undergoes stress.

When the conduit and the valve are subjected to forces such asstretching, pulling, twisting, and the like, the fluid being transferredthrough the conduit and the valve may leak or spill into theenvironment. More particularly, the conduit, rather than the ball checkvalve, is likely to rupture or otherwise malfunction in the presence ofthese forces. Thus, while the ball check valve is appropriate forchecking fluid flow, it does not prevent spillage or leakage whensubjected to external stress. Because the conduit is likely to rupture,or otherwise malfunction, in these types of situations, the spillage orleakage of fluid into the environment can be significant because thefluid flow can no longer be checked.

For example, when a fuel transport vehicle is delivering liquid througha hose into a fuel tank, one end of the hose is attached to the fueltransport vehicle, and the other end of the hose is attached to a fueltank. A valve such as a ball check valve may be disposed at the vehicleend of the hose such that fluid communication through the hose may beestablished or checked.

In the event the fuel transport vehicle drives away with the hose stillconnected, the connection will likely break or rupture. Because the hoseis typically the weakest part of the connection, the break usuallyoccurs somewhere in the hose and fluid escapes into the environment. Inthis example, the ball check valve typically does not disassemblebecause it is much stronger than the hose. Even if the ball check valvewere to break instead of the hose, fluid would still leak from thesystem. Such problems are particularly acute in the context of automatedenvironments and operations where few, or no, humans may be present, anda leak may go unnoticed for a relatively long period of time.

Another concern relates to the coupling and uncoupling of caps, valves,and other fluid system components, that are employed, for example, infuel, chemical, sewage, or other fluid transfer or processing systems.In particular, typical quick coupling devices are configured so that anoperator can uncouple the mating halves of the quick coupling device,even in the presence of line pressure. Such an arrangement isproblematic for a variety of reasons.

By way of example, in the event the line wherein the quick couplingdevice is located is charged with hazardous materials such as chemicals,sewage, fuels, or gases such as chlorine and methane, the operatorperforming the uncoupling operation could be seriously injured or killedwhen such materials escape from the line. Moreover, such hazardousmaterials are pollutants and significant time and cost is often involvedin the cleanup of such materials.

A related problem with typical quick coupling devices concerns thepressure exerted by the material in the line wherein the quick couplingdevice is located. In particular, such pressure may cause the halves ofthe quick coupling device to rapidly come apart in an uncontrolled anddangerous manner, thereby injuring the operator and/or damaging nearbyequipment. The forces resulting from such pressure can often besignificant, even where the line pressure is relatively low. Thus, in asix inch diameter (nominal) pipe for example, even a relatively lowpressure of 10 lbs./in.² (“psi”) would exert a force of about onethousand (1000) pounds on a pipe cap attached to the end of the pipe.

Not only are such pressures dangerous, but operators may not have anyway to verify, in advance of performing the uncoupling operation,whether or not the line is pressurized. Further, even if an operator isaware that pressure is present, the operator may, throughinattentiveness, negligence, or for other reasons, nevertheless attemptto uncouple the quick coupling device.

In view of the foregoing, what is needed is a fluid system componenthaving features directed to addressing the foregoing exemplaryconsiderations, as well as other considerations not disclosed herein.More particularly, an exemplary fluid system component includes featuresdirected to facilitating the secure engagement, and ready disengagement,of the mating halves of the fluid system component, while at the sametime preventing intentional or accidental disengagement of the matinghalves when a predetermined pressure is present in the line.

BRIEF SUMMARY OF AN EXEMPLARY EMBODIMENT OF THE INVENTION

In general, embodiments of the invention are concerned with a fluidsystem component that, among other things, facilitates the secureengagement, and ready disengagement, of mating halves of the fluidsystem component, while at the same time preventing intentional oraccidental disengagement of the mating halves when a predeterminedpressure is present in the line.

In one exemplary embodiment of the invention, a fluid system componentis provided that includes mating male and female halves. The male halfof the fluid system component includes a wall having an outer surfacewherein a plurality of grooves are defined. The grooves are generallyconfigured so that each of a plurality of rollers present on the outersurface of a wall of the female half of the fluid system componententers, and travels along, a corresponding groove as the male and femalehalves are rotatably engaged together.

Further, the grooves defined in the male half of the fluid systemcomponent are configured to define an angle with respect to thelongitudinal axis of the fluid system component, so that the male andfemale halves advance toward each other as they are rotatably engaged.Each of the grooves also includes a terminal segment that is connectedwith, but offset from, the intermediate and entry segments of thegroove.

In operation, the male and female portions are brought together untileach roller of the female portion has engaged a corresponding groove ofthe male portion. The two halves are then rotated in oppositedirections, causing the rollers to advance along their correspondinggrooves and thereby move the male and female halves toward each other.The two halves continue to rotate until each roller enters the terminalsegment of its corresponding groove, at which point engagement iscompleted. Thus engaged, the male and female halves cooperate to definea fluid passageway.

The introduction of a pressurized fluid into the fluid passageway actson the fluid system component in such a way that a force is exerted thatresists movement of the rollers out of the terminal segment and backinto the intermediate or entry segments of the groove. Thus, the groovegeometry affords the fluid system component the capability to use theline pressure in such a way as to prevent disengagement of the fluidsystem component halves until the line is suitably depressurized.

These and other aspects of embodiments of the present invention willbecome more fully apparent from the following description and appendedclaims.

BRIEF DESCRIPTION OF THE DRAWINGS

A more particular description of various aspects of the embodiments ofthe invention illustrated in the appended drawings will now be rendered.Understanding that such drawings depict only exemplary embodiments ofthe invention, and are not therefore to be considered limiting of thescope of the invention in any way, various features of such exemplaryembodiments will be described and explained with additional specificityand detail through the use of the accompanying drawings in which:

FIG. 1 depicts an exemplary operating environment for at least someembodiments of the present invention;

FIG. 2 is a perspective view of an embodiment of the dry break valveassembly which includes a source housing and a destination housing thatcan be releasably connected to each other using a sleeve;

FIG. 3 depicts an embodiment of a sleeve which releasably seals andconnects a source housing with a destination housing;

FIG. 4 is a perspective view indicating various details of a breakablelink assembly that is an integral portion of a collar;

FIG. 5 is a perspective cutaway view of an embodiment of the presentinvention, illustrating various features of an actuating mechanism;

FIG. 6 is a cross section view of an exemplary sealing interface withinan embodiment of a dry break valve assembly;

FIG. 7 is a perspective view illustrating various features of anexemplary embodiment of an actuating mechanism disposed within anembodiment of a dry break valve assembly;

FIG. 7A is a side view illustrating various features of an embodiment ofan actuating mechanism positioned so as to allow fluid flow through thedry break valve assembly;

FIG. 7B is a side view illustrating various features of an embodiment ofan actuating mechanism positioned so as to substantially prevent fluidflow through the dry break valve assembly;

FIG. 8 is a perspective view of an alternative embodiment of a dry breakvalve assembly depicting various features of an exemplary embodiment ofa groove arrangement that includes three grooves each of which include aterminal segment;

FIG. 8A is a section view illustrating various aspects of the exemplaryembodiment of the grooves depicted in FIG. 8;

FIG. 9 is a section view of an exemplary embodiment of a dry break valveassembly that illustrates aspects of the relation between the fluidpressure in the fluid passageway and the engagement of the first andsecond housing portions;

FIG. 10 is a top view of an exemplary embodiment of a fluid systemcomponent, specifically, a cap assembly, that includes elementsconfigured to be releasably engaged with each other;

FIG. 10A is a section view taken from the top view of FIG. 10;

FIG. 10B is a side view illustrating aspects of an exemplary groovearrangement for the cap assembly;

FIG. 11A is a top view of the exemplary cap assembly illustrated inFIGS. 10 through 10B, showing the position of various components priorto engagement of the sleeve and collar;

FIG. 11B is a top view of the exemplary cap assembly illustrated inFIGS. 10 through 10B, showing the position of various components afterengagement of the sleeve and collar; and

FIG. 12 is a side view illustrating various aspects of an exemplarygroove configuration and arrangement that includes multiple overlappinggrooves each having a plurality of intermediate segments.

DETAILED DESCRIPTION OF VARIOUS EMBODIMENTS OF THE INVENTION

Reference will now be made to figures wherein like structures will beprovided with like reference designations. It is to be understood thatthe drawings are diagrammatic and schematic representations of variousembodiments of the invention, and are not to be construed as limitingthe present invention, nor are the drawings necessarily drawn to scale.

With reference first to FIG. 1, one embodiment of a fluid transfersystem is indicated generally at 100. Note that, as contemplated herein,“fluid” includes liquids, gases, liquid-gas combinations, slurries,liquid-solid combinations, gas-solid combinations, and liquid-solid-gascombinations. In the exemplary embodiment depicted in FIG. 1, fluidtransfer system 100 includes a fluid source 102 configured for fluidcommunication with a dry break valve assembly 200. Dry break valveassembly 200, in turn, is configured for selective fluid communicationwith a fluid destination 104, by way of a fluid conduit 106.

As discussed elsewhere herein, it will be appreciated that dry breakvalve assembly 200 may be located, in its entirety, at fluid source 102,or alternatively at fluid destination 104. In one embodiment, discussedin detail below, dry break valve assembly 200 comprises at least twodiscrete portions, one of which may be located at fluid source 102, andthe other of which may be located at fluid conduit 106, or vice versa ina fluid loading situation.

As contemplated herein, the term “conduit” is meant to include anystructure or device adapted to facilitate transportation of a fluid,wherein such structures and devices include, but are not limited to,pipes, hoses, tubes, or the like. Fluid conduit 106 may be constructedof a variety of materials, or combinations thereof, including, but notlimited to, metal, plastic, rubber, and the like.

With continuing reference to FIG. 1, the fluid source 102 is illustratedas a fluid transport vehicle, and the fluid destination 104 isillustrated as an underground tank. However it will be appreciated thatfluid source 102 and/or fluid destination 104, may comprise any of avariety of different static or mobile structures and vehicles. Suchstructures and vehicles include, but are not limited to, air, water, orland vehicles, such as, but not limited to, trucks, boats, automobiles,motorcycles, ships, railcars, aircraft, and the like, as well asstructures such as tanks, reservoirs, and the like.

In operation, a pressure differential is established between fluidsource 102 and fluid destination 104 so as to cause flow of the fluidthrough fluid conduit 106 in the desired direction. It will beappreciated that the pressure differential may be established in such away as to cause flow to proceed in the opposite direction as well. Thepressure differential may result from the force of gravity, or mayalternatively be established by various types of equipment and devicesincluding, but not limited to, pumps and the like.

In general, dry break valve assembly 200 facilitates management andcontrol of fluid flow between fluid source 102 and fluid destination104. In particular, valve assembly 200 allows for selectiveestablishment and termination of fluid communication between fluidsource 102 and fluid destination 104. Additionally, dry break valveassembly 200 facilitates releasable engagement of two different fluidsystem components, for example, fluid conduit 106 and fluid source 102.Finally, dry break valve assembly 200 includes various features whichsubstantially prevent fluid leakage should the discrete portions of drybreak valve assembly 200 be separated for any reason.

With reference now to FIG. 2, dry break valve assembly 200 includes afirst housing portion 202 and second housing portion 204. As usedherein, the portion of the valve assembly closest to the fluid source isreferred to as the source housing while the other housing portion isreferred to as the destination portion. Either portion of the dry breakvalve assembly can be the source housing or the destination housing.Coupling 500 serves to removably secure first housing portion 202 andsecond housing portion 204 in a substantially leakproof engagement.

Substantially disposed within first housing portion 202 and secondhousing portion 204, respectively, are flow control assemblies 300A and300B. In general, flow control assemblies 300A and 300B facilitatemanagement of fluid flow through conduits, or the like, connected tofirst housing portion 202 and second housing portion 204, respectively.Also disposed within first housing portion 202, and discussed in greaterdetail below, is an actuating mechanism (not shown in FIG. 2), whichserves to manipulate the position of flow control assemblies 300A and300B in response to input provided by way of actuating lever 402. Thus,the position of the flow control assemblies 300A and 300B may varybetween fully open and fully closed.

First housing portion 202 includes a conduit connector 202A. Conduitconnector 202A is configured to attach to fluid conduit 106 (shown inFIG. 1), wherein such attachment may be accomplished in a variety ofways including, but not limited to, welding, brazing, soldering, and thelike. Alternatively, conduit connector 202A may comprise a compressionfitting, threaded fitting, or the like for attaching to fluid conduit106.

In similar fashion, second housing portion 204 has a conduit connector204A. Conduit connector 204A is configured to attach to fluid conduit106, wherein such attachment may be accomplished in a variety of waysincluding, but not limited to, welding, brazing, soldering, and thelike. Alternatively, conduit connector 204A may comprise a compressionfitting, threaded fitting, or the like for attaching to fluid conduit106. It will be appreciated that conduit connector 202A and/or conduitconnector 204A may, alternatively, be connected directly to fluid source102 or fluid destination 106.

Directing attention now to FIG. 3, and with continuing attention to FIG.2, additional details regarding coupling 500 are provided. As indicatedin FIG. 3, coupling 500 includes a first engaging portion 500A and asecond engaging portion 500B joined together by collar 502 which servesto substantially prevent relative motion between first engaging portion500A and a second engaging portion 500B. Preferably, first engagingportion 500A and a second engaging portion 500B each comprise an outwardextending annular ridge or the like which, when brought into aconfronting relation with each other, are collectively configured tomate with corresponding structure defined by collar 502, as suggested inFIG. 3. It will be appreciated however, that coupling 500 and collar502, either individually or collectively, may be configured in anynumber of alternate ways that would facilitate achievement of thefunctionality disclosed herein. In addition the connecting portions ofthe engaging portions 500A and 500B may be ridged to ensure thatrelative motion between the portions does not occur.

In one embodiment, first engaging portion 500A and a second engagingportion 500B each further includes a plurality of pins 504 that matewith corresponding grooves 202B and 204B, defined by first housingportion 202 and second housing portion 204, respectively. Thus, a rotarymotion imparted to coupling 500 by way of handles 506 releasably joinsfirst engaging portion 500A and a second engaging portion 500B to firsthousing portion 202 and second housing portion 204, respectively, bycausing pins 504 to travel to the respective ends of grooves 202B and204B. Preferably, grooves 202B and 204B are of such a length that arotary motion of about 90 degrees is adequate to releasably couple firsthousing portion 202 to second housing portion 204. It will beappreciated that a rotary motion of about 120 degrees in the oppositedirection will be effective to disengage coupling 500 and thus releasefirst housing portion 202 from second housing portion 204.

It will be appreciated that the arrangement of coupling 500 with respectto first housing portion 202 and second housing portion 204 may bevaried in a number of ways. For example, in one embodiment, firstengaging portion 500A is integral with first housing portion 202, sothat only second engaging portion 500B comprises pins 504.Correspondingly, only grooves 204B are present and grooves 202B are notrequired. In this embodiment, a rotation, preferably about 120 degrees,imparted to coupling 500 by way of handles 506 causes rotating pins 504,or bearings in another embodiment, to travel the length of grooves 204Bso that coupling 500 thereby releasably joins first housing portion 202to second housing portion 204.

Yet another embodiment employs essentially a reverse configuration ofthat just discussed. In particular, in this embodiment, second engagingportion 500B is integral with second housing portion 204, and only firstengaging portion 500A includes pins 504. Correspondingly, only grooves202B are present and grooves 204B are not required. In this embodiment,a rotation, preferably about 90 degrees, imparted to coupling 500 by wayof handles 506 causes pins 504 to travel the length of grooves 202B sothat coupling 500 thereby releasably joins first housing portion 202 tosecond housing portion 204.

Finally, it will be appreciated that other types of structure anddevices may be usefully employed to achieve the functionalitycollectively provided by pins 504 and grooves 202B and 204B.Accordingly, other structures and devices that provide suchfunctionality are contemplated as being within the scope of the presentinvention, wherein such other structures and devices include, but arenot limited to, threaded connections, spring-biased connections, and thelike.

Directing attention now to FIG. 4, and with continuing attention to FIG.3, additional details regarding collar 502 of coupling 500 are provided.In particular, collar 502 further includes a breakable link assembly600. Generally, breakable link assembly 600 serves two primary purposes.First, breakable link assembly 600 serves to retain collar 502 securelyin place about first engaging portion 500A and second engaging portion500B of collar 502. Further, breakable link assembly 600 includes asacrificial element that is designed to break, thereby allowing firstengaging portion 500A and second engaging portion 500B to separate fromeach other, when a force, or forces, of predetermined magnitude areapplied to particular elements of fluid transfer system 100, such as tovalve assembly 200, or to fluid conduit 106.

In effect, when the sacrificial element breaks, then the coupling 500 isno longer capable of joining the first and second housings of the valveassembly and the valve assembly disassembles into two separatecomponents. As previously described, fluid flow from each separatehousing may be checked and when the valve assembly separates in thismanner, fluid flow is checked and fluid spillage or leakage is therebyminimized.

As suggested in FIG. 4, collar 502 is essentially C-shaped, having anopening between its two ends. Breakable link assembly 600 is disposedacross the opening thus defined and includes a threaded member 602, suchas a bolt or the like, defining a bore (not shown) near one end.Preferably, the bore thus defined is substantially perpendicular to thelongitudinal axis of threaded member 602. A shear pin 604 is slidablydisposed in the bore and the opposing ends of shear pin 604 are receivedin collar 502 as indicated. Preferably, shear pin 604 is prevented fromexiting the bore by way of cotter pins 606, or the like, disposed ateither end of shear pin 604. It will be appreciated that shear pin 604may alternatively be glued, welded, brazed, or otherwise bonded tocollar 502 so as to prevent it from exiting the bore in threaded member602.

Breakable link assembly 600 further includes a nut 608, or the like,engaged for advancement along threaded member 602. In operation, nut 608is rotated so as to advance along threaded member 602 and thus draw theopposing ends of collar 502 securely together.

The operation of breakable link assembly 600 proceeds generally asfollows. In the event a force, or forces, of predetermined magnitude ineither a tensile or axial load are applied to valve assembly 200 and/orto fluid conduit 106, shear pin 604 will fracture and the valve assemblywill disassemble. It will be appreciated that the materials and/orgeometry of shear pin 604 may desirably be varied to adjust the point atwhich fracture will occur. It will further be appreciated thatsacrificial elements other than shear pin 604 may usefully be employed.In general, any sacrificial element and/or breakable link assembly thatprovides the functionality, disclosed herein, of shear pin 604 and/orbreakable link assembly 600 is contemplated as being within the scope ofthe present invention.

Upon fracture of shear pin 604, threaded member separates from collar502, thus permitting the ends of collar 502 to move apart and therebyallow separation of first housing portion 202 and second housing portion204. The functionality provided by breakable link assembly 600 thusensures that in the event a predetermined level of force is applied todry break valve assembly 200, or to components to which it is connected,dry break valve assembly 200 will break dry, and thus substantiallyprevent any material leakage of fluid. Further, breakable link assembly600 substantially ensures that in the event such forces are applied, nomaterial damage occurs to the components of fluid transfer system 100(see FIG. 1). Thus, in addition to minimizing the fluid loss that wouldotherwise occur, the conduit 106 is preserved and damage is not done tothe fluid source or the fluid destination.

Note that a variety of means may be profitably employed to perform thefunctions enumerated herein, of sealingly engaging first housing 204with second housing 206 using coupler 500. Coupler 500 is an example ofmeans for sealingly engaging first housing portion 202 and secondhousing portion 204. Accordingly, the structure disclosed herein simplyrepresents one embodiment of structure capable of performing thisfunction. It should be understood that this structure is presentedsolely by way of example and should not be construed as limiting thescope of the present invention in any way.

The valve assembly 200 and its various parts may be made of a range ofmaterials depending on the type of fluid being transferred. Preferably,a material is chosen that can withstand corrosion and high temperaturethermal cycling, such as carbon steel or stainless steel. Generally,valve assembly 200 may be constructed from Austenitic steel.

FIG. 5 shows an exploded perspective view of various features of theflow control assemblies of valve assembly 200. The following descriptionof the housing configuration and flow control assemblies is byillustration only and not by way of limitation. Generally, flow controlassembly 300A may comprise a flow control member 302A, a guide 322A, aresilient member 344A, a fitting member 348, and a snap ring 364A.Similarly, flow control assembly 300B may comprise a flow control member302B, a guide 322B, a resilient member 344B, a sealing member 350, and asnap ring 364B.

Flow control assemblies 300A and 300B have a flow control member 302Aand 302B, respectively. As shown in FIG. 3, flow control members 302Aand 302B have a round disc-like valve gate 304A and 304B, respectively.Valve gate 304A contains a bore 320 substantially in the center of thevalve gate so as to allow a substantially cylindrical piece to passthrough the bore. It will be understood that bore 320 may be anygeometrical shape (e.g., square, rectangular, polygonal, etc.) that willallow passage of a corresponding geometrical-shaped piece to passthrough the bore.

Attached to valve gate 304A is a hollow driver shaft 316. Driver shaft316 is placed in transverse relation to valve gate 304B. Preferably,driver shaft 316 is substantially concentric with bore 320 and containssubstantially the same geometric shape as bore 320. Attached to valvegate 304B is a member 318, which may be solid or hollow. Driver shaft316 and member 318 may be attached to valve gate 304A and 304B by anymeans known in the art, such as, but not limited to, welding, adhesivebonding, or may be formed integrally with valve gates 304A and 304B.

FIG. 5 further illustrates guides 322A and 322B. Guides 322A and 322Bessentially add structural support to flow control assemblies 300A and300B. Guides 322A and 322B contain bores 326A and 326B whose innerdiameters correspond respectively with the outer diameters of drivershaft 316 and member 318. In practice, driver shaft 316 slidably passesthrough bore 326A, and, similarly, member 318 slidably passes throughbore 326B. Preferably, guides 322A and 322B are essentially hollowexcept for three support bars generally designated as 340A and 340B. Thehollow structure allows for structural members to pass through guides322A and 322B and to be movably connected to valve gates 304A and 304B,which will be discussed in further detail later in this specification.However, it will be appreciated that guides 322A and 322B may beconstructed having a partially solid configuration as long as therequisite area is present to allow for movement of parts.

FIG. 5 shows resilient member 344A and 344B which are placed onto drivershaft 316 and solid member 318, respectively. Resilient members 344A and344B are shown in FIG. 5 to be springs. However, one skilled in the artwill understand that resilient members 344A and 344B may be anystructure which maintains a bias such as, but not limited to, a rubbermaterial, an elastic material, polished metal, and the like.

FIG. 5 further depicts fitting member 348 and corresponding sealingmember 350. The configuration of fitting member 348 and sealing member350 will be discussed in more detail later in this specification.However, in general terms, fitting member 348 is tapered on one side toprovide a valve seat for valve gate 302A. Similarly, sealing member 350is tapered on one side to provide a valve seat for valve gate 302B.Preferably, valve gates 302A and 302B have corresponding tapers to allowfor better sealing engagement.

As shown in FIG. 2, first housing portion 202 and second housing portion204 are configured to allow for placement of flow control assemblies300A and 300B to be disposed substantially within each housing. FIG. 5shows ridge 360 placed on the interior surface of first housing portion202. Ridge 360 acts as structural support for flow control assembly300A. During assembly, guide 322A rests on ridge 360. Resilient member344A is slid onto driver shaft 316, after which flow control member 302Ais placed into first housing portion 202 with driver shaft 316 passingthrough bore 326A. Finally, fitting member 348 is placed into firsthousing portion 202 to complete the flow control assembly 300A. It willbe understood from the drawings and foregoing discussion that flowcontrol assembly 300B may be assembled in a manner similar to that forflow control assembly 300A.

It will be noted from FIG. 5, that second housing portion 204 has aledge 362 to provide a similar structural function as ridge 360. It willbe appreciated that first housing portion 202 and second housing portion204 may have structural ridges and grooves on the interior surface ofthe housing to provide for better structural engagement of correspondingparts of flow control assemblies 300A and 300B.

In one embodiment, snap rings 364A and 364B are provided for a bettersealing engagement when flow control assembly 300A and 300B areassembled and for easier disassembly during maintenance of the valveassembly. In another embodiment, valve gate 304A and 304B may have anO-ring placed along the taper to provide for better sealing engagement.

FIG. 6 is a cross-section of an exemplary embodiment of the dry breakvalve assembly, illustrating the sealing engagement between firsthousing portion 202 and second housing portion 204. First housingportion 202 and second housing portion 204 are joined in sealingengagement preferably in at least two ways—at their outer rims andbetween fitting member 348 and sealing member 350.

FIG. 6 shows the outer rims of first housing portion 202 and secondhousing portion 204 in sealing engagement. During assembly of dry breakvalve assembly 200, coupler 500 acts to join the outer rims of firsthousing portion 202 and second housing portion 204 to join them insealing engagement. Tightening of the coupler 500 further acts to sealvalve assembly 200. Preferably, L-shaped grooves 204B are configuredsuch that sealing engagement occurs when pins 504 are engaged withL-shaped grooves 204B.

Preferably, a sealing feature is also provided between fitting member348 and sealing member 350. As shown in FIG. 6, fitting member 348 isprovided with a tapered ridge 368 running circumferentially aroundfitting member 348. Similarly, sealing member 350 is provided with acorresponding tapered channel 370 running circumferentially aroundsealing member 350. The terms “peripheral” and “circumferential” areadopted herewith to describe tapered ridge 368 and tapered channel 370since tapered ridge 368 is disposed around the perimeter of an interiorcavity formed within fitting member 348. Thus, peripheral tapered ridge368 peripherally defines the opening of a cavity formed through fittingmember 350. By providing ridge 368 and channel 370 with taperedsurfaces, greater surface area is provided which allows an improvedsealing engagement without increasing the diameter of the embodiment asis required, for example, to increase the sealing surface area whenusing a common flange joint.

Coupler 500 is provided with compressing edge 372 which biasescompensating washer(s) 374 against abutting edge 376 of fitting member348. Coupler 500 attaches to the external surface of sealing member 350by the twist coupling method discussed previously and described in moredetail hereinafter. Compensating washer(s) 374, shown best in FIG. 6,serves a dual purpose. Compensating washer(s) 374 provides compensationdue to “creeping” (degradation of the seal due to thermal contraction)which occurs at low temperatures. Compensating washer(s) 374 also servesto bias coupler 500 in a direction which will hold pins 504 in theL-shaped grooves 204B and thus provides the tension necessary for properoperation of the twist coupling. In this regard, when pins 504 areseated in the L-shaped grooves 204B, compensating washer(s) 374 biasesfitting member 348 towards sealing member 350, and thus assists informing a proper seal.

As can be seen best in FIG. 6, fitting member 348 is provided with anabutting edge 376 while coupler 500 is provided with a compressing edge372. One pin 504 and L-shaped groove 204B can be seen in the lowerportion of FIG. 6. Compensating washer(s) 374 is positioned so thatcompressing edge 372 and abutting edge 376 are urged apart. Pins 504,grooves 204B, and compensating washer(s) 374, are arranged such thatsealing contact between tapered ridge 368 and tapered channel 370 occurswhen pins 504 are situated in grooves 204B. This arrangement providesthat when pins 504 are received in the grooves 204B, compensatingwasher(s) 374 is partially or fully compressed.

It should be understood that compensating washer(s) 374 may be replacedby structures other than that shown and described in connection withFIG. 6 above. For example, if the embodiment is to be used only undermoderate temperature and pressure conditions, compensating washer(s) 374may be a washer of a resilient or elastic material, such as rubber.Depending upon the application, those skilled in the art will be able todetermine what alternative structures and materials may be used forcompensating washer(s) 374. The washer(s) 374 is preferably compressibleso as to allow pins 504 to seat in grooves 204B while urging taperedridge 368 into sealing engagement with tapered channel 370. Thisarrangement provides a coupling which is highly resistant to looseningdue to vibration.

By the above-described arrangement, tapered ridge 368 is held in tightsealing arrangement with tapered channel 370. Note that a variety ofmeans may be profitably employed to perform the functions enumeratedherein, of providing a sealing engagement between first housing portion202 and second housing portion 204. Fitting member 348 and sealingmember 350 are examples of means for sealingly engaging first housingportion 202 and second housing portion 204. Accordingly, the structuredisclosed herein simply represents one embodiment of structure capableof performing these functions. It should be understood that thisstructure is presented solely by way of example and should not beconstrued as limiting the scope of the present invention in any way.

In one embodiment, an actuating mechanism is used to operate the flowcontrol assemblies 300A and 300B. FIG. 7 illustrates a perspective viewof an actuating mechanism 501. Preferably, actuating mechanism 501 usescam action in operation. Cam action refers generally to a sliding piecein a mechanical linkage used especially in transforming rotary motioninto linear motion or vice versa.

As depicted in FIG. 7, actuating mechanism 501 has a cam handle 503. Camhandle 503 provides three attachment sites, 512, 516A, and 516B.Attached to site 512 is cam arm 518, which in turn is connected todriver 505 at attachment site 514. Driver 505 has a first end 526 and asecond end 528. Driver 505 is shown in FIG. 7 to be essentiallycylindrical in shape. However, it will be understood that driver 505 maybe any geometric shape which will correspond with driver shaft 316 andguide bore 326A. Driver 505 is essentially a mechanical piece forimparting motion to components of the dry break valve assembly as willbe discussed in further detail later in the specification. Attached tosites 516A and 516B are displacement shafts 506A and 506B. Displacementshafts 506A and 506B are shown in FIG. 7 to be essentially rectangularin shape. However, it will be understood that displacement shafts 506Aand 506B may be manufactured in any geometric shape, such ascylindrical, elliptical, square, and the like, without departing fromthe scope of the present invention.

Preferably the connections of driver 505 and displacement shafts 506Aand 506B to cam handle 503 at sites 512, 516A and 516B are pinconnections such that the parts may be movably connected. However, itwill be understood that such connections may be done in a variety ofways known to the art including, but not limited to a bolt, a screw,pins, and the like.

As shown in FIG. 2, cam handle 402, also referred to as an actuatinglever, is connected to an actuating arm 510, which, in turn, isconnected to an actuating lever 508. Actuating arm 510 is substantiallydisposed within first housing portion 202. Actuating arm 510 ispreferably placed such that it is substantially over the center ofactuating mechanism 501. Preferably actuating arm 510 and cam handle 503are connected such that cam handle 503 cannot move independently ofactuating arm 510.

FIG. 7 also shows valve gates 304A and 304B in relation to actuatingmechanism 501. Valve gate 304A is shown operably connected to actuatingmechanism 501 while valve gate 304B is disposed in operative relation tothe actuating mechanism. Actuating mechanism 501 effects motion in bothvalve gate 304A and 304B at substantially the same time.

Valve gate 304A is shown with second end 528 of driver 505 disposedthrough bore 320. Preferably, in the resting position, second end 528 issubstantially disposed within bore 320. However, it will be understoodthat second end 528 may be partly out of bore 320 without departing fromthe scope of the present invention. The driver 505 is sized to slidablypass through bore 320 without substantial obstruction from bore 320.

Displacement shafts 506A and 506B are shown to be connected to valvegate 304A at attachment sites 520A and 520B. Bore 320 and sites 520A and520B are placed in a triangular configuration with sites 520A and 520Bbeing placed substantially equidistant from bore 320. Sites 520A and520B are also placed substantially equidistant from actuating arm 510such that displacement shafts 506A and 506B are in substantial alignmentwith one another. Preferably the connections between displacement shafts506A and 506B and connection sites 520A and 520B are pin connectionssuch that the parts may be movably connected. However, it will beunderstood that the parts may be connected by known means in the art,such as, but not limited to, welding, bolting, and the like, withoutexceeding from scope of the present invention.

Referring now to FIGS. 7A and 7B, the operation of actuating mechanism501 will be discussed in detail. FIG. 7A shows a side view of actuatingmechanism 501 at rest. Attachment site 512, cam arm 518, and attachmentsite 514 create a joint 530. Generally, actuating mechanism 501 operatesas follows: the operator depresses the actuating lever 402 (shown inFIG. 2) and then the operator rotates actuating lever 402 whichtransmits a torque force (TF) through actuating arm 510 (not shown). Thetorque force (TF) is shown in FIG. 7B in the direction of the arrows.Such torque force (TF) rotates cam handle 503 which in turn rotatessites 512, 516A, and 516B (not shown). Thus, driver 505, anddisplacement shafts 506A and 506B (not shown) will be in motion atsubstantially the same time.

As cam handle 503 rotates, site 512 rotates in a downward directionforcing motion through cam arm 518 and, in turn, forcing driver 505 in adownward direction. Driver 505 passes through bore 320 such that secondend 528 of the driver comes into contact with valve gate 304B. Thedownward motion of driver 505 pushes against valve gate 304B, whichdisplaces valve gate 304B. The displacement of valve gate 304B forcesresilient member 344B in a biased position. In one embodiment, locatedsubstantially at the center of valve gate 304B is a groove 524. Theshape of groove 524 corresponds with the geometric shape of the end faceof driver 505 such that driver 505 engages groove 524.

At substantially the same time as site 512 is in motion, sites 516A and516B are rotating in an upward direction, thus pulling displacementshafts 506A and 506B in an upward direction. This upward motion pulls atattachment sites 520A and 520B (not shown), which in turn pulls valvegate 304A upward, displacing valve gate 304A. The displacement of valvegate 304A forces resilient member 344A in a biased position. Thus, atsubstantially the same time, valve gates 304A and 304B are displaced oropened to establish fluid communication between the valve gates. FIG. 7Bshows a side view of the actuating mechanism in full operation (i.e.,fully opened) with valve gates 304A and 304B being displaced or opened.Thus, at least indirectly, actuating mechanism 501 acts to open bothvalve gates 304A and 304B at substantially the same time.

When actuating mechanism 501 is in fully open, with valve assembly 200completely assembled, actuating mechanism 501 will lock into placeautomatically. This automatic locking feature is provided by theequilibrium of forces provided by the torque force (TF) and an equal andopposite retention force (RF) created by resilient member 344B. Duringactuation, cam arm 518 acts to shift attachment site 512 from attachmentsite 514, such that the sites are offset from one another as shown inFIG. 7B.

In other words, when actuating mechanism 501 is completely actuated,joint 530 is in an overextended position. When actuating mechanism 501is fully actuated, resilient member 344B is depressed in a biasedposition. The retention force (RF) created by biased resilient member344B acts upwardly through valve gate 304B to driver 505 to keep joint530 locked in an overextended position. Once the retention force (RF) isapplied, the torque force (TF) is no longer required and actuatingmechanism 501 will remain locked until the retention force (RF) isremoved. Thus, the present invention provides for an automatic lockingmechanism when the actuating mechanism 501 is fully opened and dry breakvalve assembly 200 is fully assembled.

In one embodiment, dry break valve assembly 200 has an automatic checkvalve feature (i.e., fail closed feature). When the sealing engagementbetween first housing portion 202 and second housing portion 204 isbroken, valve assembly 200 automatically closes to prevent substantialleakage of fluid. As discussed above, valve gates 304A and 304B aremaintained in the open position by applying a torque force (TF) and/or aretention force (RF). When actuating mechanism 501 is fully activated,and the torque force (TF) is removed, actuating mechanism 501 remainslocked due to the retention force (RF) as discussed above. Releasing theretention force (RF) will cause actuating mechanism 501 to automaticallyclose. Essentially, if no torque force (TF) or retention force (RF) isapplied, actuating mechanism 501 is predisposed to spring back into itsoriginal position because resilient members 344A and 344B are biased inthe closed position, i.e., valve gates 304A and 304B close atsubstantially the same time. Release of the retention force (RF) mayoccur when first housing portion 202 is separated from sealingengagement with second housing portion 204. It will be understood thatseparation of first housing portion 202 from second housing portion 204may occur manually or automatically. Thus, the present inventionprovides for automatic checking of fluid flow whenever the valveassembly is disassembled, whether automatically or manually.

While, in the case of some embodiments disclosed herein, it is useful toprovide a fluid system component, such as a dry break valve assembly,having mating halves, or portions, that can be readily engaged anddisengaged under a variety of pressure conditions, it is useful in othersituations to be able to prevent disengagement of the mating portions ofthe dry break valve when the pressure in the line wherein the dry breakvalve is employed has exceeded, or dropped below, as applicable, apredetermined level. With the foregoing in view, attention is directednow to FIG. 8 wherein various details are provided regarding aspects ofan alternative embodiment of the dry break valve assembly, generallydenoted at 700. As the operational and structural aspects of theillustrated embodiment are similar in many regards to those of otherembodiments disclosed herein, the following discussion will focusprimarily on selected aspects of the illustrated embodiment.

In particular, the dry break valve assembly 700 includes a first housingportion 702 and second housing portion 704 removably joined together bya coupling 800. While, in the illustrated embodiment, coupling 800 isintegral with first housing portion 702, coupling 800 comprises acomponent discrete from both first housing portion 702 and secondhousing portion 704 in some alternative embodiments. Note that, asdiscussed elsewhere herein, the use of coupling 800 is not limited todry break valve assembly 700

With continuing reference to aspects of the first and second housingportions, the first housing portion 702 and second housing portion 704each include a corresponding conduit connector 702A and 704A,respectively, configured to attach to a fluid conduit 106 (FIG. 1) orother fluid system component, wherein such attachment may beaccomplished in a variety of ways including, but not limited to,welding, brazing and soldering. Other exemplary types of conduitconnectors 702A and 704A that may be employed include compressionfittings and threaded fittings.

As indicated in the exemplary embodiment illustrated in FIG. 8, thefirst housing portion 702 and second housing portion 704 each furtherinclude a corresponding flow control assembly 900A and 900B,respectively, that are operated by way of an actuating mechanism (see,e.g., FIG. 7) and associated actuating lever 706, as described elsewhereherein. As discussed in further detail below, rotary motion for engagingand disengaging first housing portion 702 and second housing portion 704is imparted by way of handles 802 joined to coupling 800.

In general, the engagement of first housing portion 702 and secondhousing portion 704 is achieved by way of mating pins and grooves,aspects of which are illustrated in FIG. 8. More specifically, coupling800 includes three engagement members, such as pins 804, spaced aboutits circumference and configured and arranged to engage second housingportion 704, as discussed below. In an alternative embodiment discussedherein, pins 804 are replaced with a plurality of rollers connected tocoupling 800. The use of rollers in place of pins is useful, forexample, where coupling 800 is relatively large, and significantfrictional forces must otherwise be overcome to operate coupling 800 inthe manner described below.

In correspondence with pins 804, second housing portion 704 includesthree grooves 708, each traversing an arc β of about one hundred twenty(120) degrees about the circumference of second housing portion 704. Thewidth and depth of grooves 708 generally correspond to the diameter andlength, respectively, of pins 804. In the illustrated embodiment, eachgroove 708 includes three connected portions, or segments. Specifically,each groove 708 includes an entry segment 708A, an intermediate segment708B, and a terminal segment 708C. In some alternative embodiments,grooves 708 are defined by a structure that is discrete from, butattached or attachable to, second housing portion 704. In someembodiments, the terminal segment comprises a segment of a groove, otherthan the entry segment, that cooperates with a longitudinal axis such asaxis AA (see, for example, FIG. 8A) to define an oblique angle. In yetother embodiments, the terminal segment may be generally perpendicularto a longitudinal axis (see, for example, FIG. 12). Moreover, the numberand arrangement of intermediate segments in a groove, or grooves, may bevaried as/if desired (see, for example, FIGS. 8A and 12).

It should be noted that the foregoing configuration is exemplary onlyand aspects such as, but not limited to, the size, number, geometry,arrangement, offset angle θ and arc length β (of grooves 708) anddisposition of one or more of the embodiments of the pins and groovesdisclosed herein, including pins 804 and grooves 708, may be modified asnecessary to suit the requirements of a particular application.Consistent with the foregoing, details concerning various alternativeembodiments of grooves are set forth elsewhere herein (see FIG. 12).Moreover, at least one embodiment of the invention includes fourengagement members, examples of which include pins 804 and rollers 1106A(FIG. 10A).

In general, the engagement of first housing portion 702 and secondhousing portion 704 is effected by positioning each pin 804 in acorresponding groove 708 and causing pins 804 to travel along grooves708, as suggested in FIG. 8A. More particularly, first housing portion702 and second housing portion 704 are brought together until each pin804 of coupling 800 is positioned in the entry segment 708A of acorresponding groove 708 of second housing portion 704. Rotation ofsecond housing portion 704 is then initiated, by way of handles 802. Asa result of the angular orientation of entry segments 708A with respectto a longitudinal axis AA defined by the dry break valve assembly 700,the initial rotation of first housing portion 702 causes second housingportion 704 to be drawn toward first housing portion 702.

Continued rotation of first housing portion 702 causes pins 804 tocomplete their traverse of corresponding entry segments 708A, and moveinto their respective intermediate segments 708B. In at least somecases, pins 804 travel to the respective ends of intermediate segments708B. In any event, pins 804 remain in intermediate segments 708B untilsuch time as a predetermined pressure level is attained in a fluidpassageway 1000 (FIG. 9) collectively defined by first housing portion702 and second housing portion 704.

With continuing reference to FIGS. 8 and 8A, and directing attention nowto FIG. 9, details are provided concerning various operational aspectsof an exemplary embodiment of dry break valve assembly 700. As suggestedabove, the engagement of first housing portion 702 and second housingportion 704 results in the definition of a fluid passageway, generallydenoted at 1000 in FIG. 9, and comprising portions 1000A and 1000B.

Prior to commencement of a fluid transfer operation, fluid is introducedinto portion 1000A, for example, by way of a conduit 106 (FIG. 1)connected to first housing portion 702, thereby pressurizing portion1000A. The pressure thus exerted, denoted at P₁ in FIG. 10, acts on theback of valve gate 304A, which is in contact with sealing member 348attached to first housing portion 702. As a result of this arrangementof valve gate 304A, sealing member 348, and first housing portion 702,the exertion of P₁ in this way causes first housing portion 702 to moveslightly forward into closer engagement with second housing portion 704,thereby forcing pins 804 to lock up into corresponding terminal segments708C of grooves 708, as suggested in FIG. 8A.

In the illustrated embodiment, the forward motion of first housingportion 702 may, depending on the position of pins 804 prior topressurization of portion 1000A, be accompanied by a rotary motion offirst housing portion 702 as well, as pins 804 travel along intermediatesegment 708B and come to rest in terminal segment 708C of groove 708.Further, one or both of first housing portion 702 and second housingportion 704 may or may not rotate, depending upon whether one or bothsuch portions 702 and 704 are otherwise restrained from rotationalmovement during the initial pressurization of portion 1000A of fluidpassageway 1000. In yet other embodiments, little or no rotation offirst housing portion 702 or second housing portion 704 occurs.

As suggested in FIG. 8A, rotary motion of first housing portion 702, atleast, is facilitated, at least in part, by the geometric relation ofintermediate segment 708B with terminal segment 708C, expressed as anoffset angle θ. Specifically, as the action of pressure P₁ on the backof valve gate 304A (FIG. 9) causes first housing portion 702 to moveforward into closer engagement with second housing portion 704, thegeometry that defines offset angle θ guides each pin 804 laterally, aswell as forward, from the intermediate segment 708B into itscorresponding terminal segment 708C.

Once pins 804 are seated thus, the continuing exertion of pressure P₁ onthe back of valve gate 304A aids in the retention of pins 804 in theircorresponding terminal segments 708C (FIG. 8A) and resists motion ofpins 804 in the opposite direction, that is, out of their correspondingterminal segments 708C. As a result, first housing portion 702 andsecond housing portion 704 of dry break valve assembly 700 cannot bedisengaged from each other until the fluid pressure in portion 1000A offluid passageway 1000 has been reduced to a predetermined level ordifferential, or until the pressure in portions 1000A and 1000B has beenequalized. Thus, the pins 804 and grooves 708 cooperate with each other,and advantageously employ the line pressure, to ensure a secureconnection between first housing portion 702 and second housing portion704 of dry break valve assembly 700 under a variety of pressureconditions. Note that the arrangement and configuration of pins 804 andgrooves 708 in this exemplary embodiment, and others disclosed herein,may be varied to function in concert with either positive or negative(vacuum) pressures in fluid passageway 1000.

Note further that a variety of means may be profitably employed toperform the functions, disclosed herein, of pins 804 and grooves 708,and rollers 1106A and grooves 1102C discussed below. Examples of suchfunctions include, but are not limited to, releasably engaging first andsecond elements of a fluid system component, maintaining engagement ofsuch first and second elements so long as the line fluid pressure meetsor exceeds a first predetermined value, and facilitating disengagementof such first and second elements when the line fluid pressure hasreached a second predetermined value. Such first and second elements ofa fluid system include, but are not limited to, first housing portion702 and second housing portion 704 of dry break valve assembly 700, andsleeve 1102 and collar 1106 of cap assembly 1100. Thus, pins 804 andgrooves 708, and rollers 1106A and grooves 1102C, respectively, compriseexemplary structures that function as a means for releasable engagement.It should be understood that such structures are presented solely by wayof example and should not be construed as limiting the scope of thepresent invention in anyway.

While, in the foregoing discussion, various operational aspects of anexemplary embodiment of dry break valve assembly 700 are considered inthe situation wherein a fluid processing operation is initiated bypressurization of portion 1000A of fluid passageway 1000, yet otherfluid processing operations are commenced by initially pressurizingportion 1000B of fluid passageway 1000. As discussed below however, pins804 and grooves 708 provide comparable functionality regardless of whichportion of fluid passageway 1000 is initially pressurized.

In particular, fluid introduced into portion 1000B of fluid passageway1000 prior to commencement of a fluid transfer operation serves topressurized portion 1000B. The pressure thus exerted, denoted at P₂ inFIG. 9, acts on the back of valve gate 304B, which is in contact withsealing member 350 attached to second housing portion 704. As a resultof this arrangement of valve gate 304B, sealing member 350, and secondhousing portion 704, the exertion of P₂ in this way causes secondhousing portion 704 to move slightly forward into closer engagement withfirst housing portion 702, thereby forcing terminal segments 708C ofgrooves 708 into engagement with corresponding pins 804, as suggested inFIG. 8A.

Similar to the case where portion 1000A is initially pressurized, thepressurization of portion 1000B may, depending on the position of pins804 and terminal segments 708C prior to such pressurization, beaccompanied by a rotary motion of second housing portion 704 as well, asterminal segments 708C of groove 708 travel into a position where theycan engage corresponding pins 804. Of course, one or both of firsthousing portion 702 and second housing portion 704 may or may notrotate, depending upon whether one or both such portions 702 and 704 areotherwise restrained from rotational movement during the initialpressurization of portion 1000B of fluid passageway 1000. In any event,initial pressurization of portion 1000B will operate, in substantiallythe same fashion as initial pressurization of portion 1000A, withrespect to the engagement of first housing portion 702 with secondhousing portion 704.

While the immediately preceding discussion is concerned with a specifictype of fluid system component, that is, a dry break valve, embodimentsof the invention are directed, more generally, to any fluid systemcomponent having portions, or elements, which are desired to bereleasably engaged. One exemplary embodiment of such a fluid systemcomponent is considered below.

Directing attention now to FIGS. 10 through 10B, details are providedconcerning an exemplary embodiment of a cap assembly, generally denotedat 1100. In the illustrated embodiment, cap assembly 1100 generallyincludes a sleeve 1102, configured to receive the end of a fluid conduit1200, a cap 1104 configured to be positioned on the end of fluid conduit1200 and cooperating with fluid conduit 1200 to at least partiallydefine a fluid passageway 1300 when so positioned, and a collar 1106generally configured to retain cap 1104 in position.

More particularly, sleeve 1102 defines a socket 1102A having an insidediameter of dimension ID compatible with the outside diameter dimensionOD of fluid conduit 1200. It is desirable in some cases to constructsleeve 1102 in such a way that a gap is introduced between the inside ofsocket 1102A and fluid conduit 1200 so as to accommodate, for example,any differences in the thermal expansion rates of sleeve 1102 and fluidconduit 1200. The sleeve 1102 may be attached to fluid conduit 1200 inany suitable manner, such as by methods including, but not limited to,welding, brazing and soldering. In at least one embodiment, sleeve 1102and fluid conduit 1200 each include mating threads so that sleeve 1102can be removably attached to fluid conduit 1200.

Generally, sleeve 1102 comprises a metallic material that, in at leastsome instances, is chemically and thermally compatible with fluidconduit 1200. Exemplary materials for sleeve 1102 include, but are notlimited to, copper and its alloys, steels, iron, aluminum and itsalloys, and titanium and its alloys. Moreover, sleeve 102 may bemachined or cast. Other suitable construction methods may alternativelybe employed.

With continuing reference to its various geometric features, sleeve 1102further includes a substantially annular chamfer 1102B that defines anopening wherein a portion of cap 1104 is received, as indicated in FIG.10A. Generally, the geometry of chamfer 1102B is configured tocorrespond to the structure of cap 1104 with which it interfaces.Geometric aspects of chamfer 1102B such as, but not limited to, the wallthickness and chamfer angle may be adjusted as necessary to suit therequirements of a particular application.

As further indicated in FIG. 10A, sleeve 1102 defines a plurality ofgrooves 1102C that are configured and arranged to engage correspondingstructure of coupling 1106, discussed in further detail below. Inparticular, and directing attention now to FIG. 110B as well, eachgroove 1102C includes three connected segments, an entry segment 1102D,an intermediate segment 1102E, and a terminal segment 1102F. Suchgrooves may be (a z machined, or otherwise formed, in the outer surfaceof sleeve 1102 and, in one embodiment, each describes an arc β of aboutone hundred twenty (120) degrees about the circumference of sleeve 1102.In the case of other exemplary embodiments, such as that illustrated inFIG. 12 for example, arc β described by each groove may be such that thegrooves overlap each other. Similar to other exemplary embodiments ofgrooves disclosed herein, intermediate segment 1102E and terminalsegment 1102F cooperate to define an offset angle δ that aids in theengagement of collar 1106 with sleeve 1102 generally in the mannerdescribed elsewhere herein.

It should be noted that the embodiment of grooves 1102C illustrated inFIG. 10B is exemplary only and aspects of grooves 1102C such as, but notlimited to, the size, number, geometry, arrangement, arc length β,offset angle δ, and disposition of one or more of grooves 1102C may bevaried in accordance with the requirements of a particular application.Accordingly, such exemplary embodiment should not be construed to limitthe scope of the invention in any way.

In correspondence with the grooves 1102C defined by sleeve 1102, collar1106 includes a plurality of rollers 1106A, each of which is configuredand arranged to be received within a corresponding groove 1102C and totravel therealong, as suggested by the exemplary roller travel pathsillustrated in FIG. 10B. To that end, each roller 1106A has a diameterand thickness that generally correspond with the width and depth,respectively, of a corresponding groove 1102C. As indicated in FIG. 10A,the rollers 1106A are disposed within the interior of collar 1106 andare each attached to a corresponding fastener 1106B that passes throughcollar 1106. Each of the fasteners 1106B is secured in position by acorresponding nut 1106C, and the extent to which rollers 1106A protrudeinto the interior of collar 1106 may be changed by adjusting thepositioning of nuts 1106C accordingly. In some embodiments of theinvention, bearings or similar structures or devices are provided tofacilitate ready and reliable rotation of the rollers 1106A.

With continuing attention to FIG. 10A, further details are providedconcerning aspects of collar 1106. In particular, collar 1106 defines asealing surface 1106D that cooperates with O-ring 1108 to substantiallyprevent fluid leakage from the joint cooperatively defined by cap 1104and collar 1106, as well as from the joint cooperatively defined by cap1104 and sleeve 1102. As suggested by the foregoing, and as illustratedin FIG. 10A, the exemplary embodiment of collar 1106 is substantiallyhollow and is configured to receive cap 1104 in such a way as tosubstantially prevent material axial or radial movement of cap 1104 whencollar 1106 has fully engaged sleeve 1102, as shown in FIG. 10A.

In the illustrated embodiment, cap 1104 and collar 1106 comprisediscrete structures. However, in an alternative embodiment, cap 1104 andcollar 1106 are integral with each other, or otherwise permanentlyjoined to each other, and an O-ring or other sealing device isinterposed between cap 1104 and sleeve 1102. The foregoing arrangementsare exemplary only however, and are not intended to limit the scope ofthe invention.

With continuing reference to FIGS. 10 through 10B, and directingattention now to FIGS. 11A through 11C, cap assembly 1100 furtherincludes one or more handles 1110 that permit a user to impart a rotarymotion so as to engage (FIG. 11B), or disengage (FIG. 11A), collar 1106and sleeve 1102. The handles 1106E may comprise steel bar stock or anyother suitable materials and/or configurations. In at least oneembodiment, aspects of which are illustrated in FIG. 11C, each ofhandles 1110 are rotatably attached, by way of pins 1112, tocorresponding blocks 1114 joined to collar 1106 so that handles 1110 canbe rotated, as indicated, from a use position upward into a storageposition when not needed, and vice versa. Moreover, some embodimentsinclude one or more stops 1115 which serve to prevent over-rotation ofcollar 1106. In the embodiment illustrated in FIG. 10A, stops 1115comprise bolts that pass through collar 1106. However, any othersuitable arrangement or structure providing similar functionality mayalternatively be employed.

As further indicated in FIGS. 10A, 11A and 11B, cap assembly 1100further includes an alignment tab 1116, which is attached to sleeve 1102and/or fluid conduit 1200, or otherwise suitably located. In theillustrated embodiment, alignment tab 1116 defines an opening 1116Apositioned to be aligned with a corresponding opening 1106B1 defined byone of the fasteners 1106. At such time as an opening 1106B1 issubstantially aligned with opening 1116A in a way that corresponds to adesired position of handles 1110, a tamper-evident device 1118comprising, for example, a thin wire 1118A that can be threaded throughthe aligned holes and securely fastened with a lead seal 1118B so thatan observer can readily determine if the position of handles 1110 hasbeen changed subsequent to placement of the tamper-evident device 1118.

Moreover, and as suggested above, alignment tab 1116 is positioned so asto provide feedback to the operator as to whether or not collar 1106 andsleeve 1102 are fully engaged with each other. In particular, and asindicated in FIG. 11A, collar 1106 is initially positioned so that afastener 1106 is disposed on either side thereof. As collar 1106 isrotated to the fully engaged position, illustrated in FIG. 11B, the hole1116A of alignment tab 1116 is aligned with a corresponding hole 1106B1of a fastener 1106B. Consequently, an operator can readily make a visualdetermination as to whether or not collar 1106 and sleeve 1102 are fullyengaged with each other.

In some embodiments, cap assembly 1100 additionally includes a safetyrestraint 1120 comprising a cable 1120A and cable crimps 1120B. In anexemplary embodiment, cable 1120A comprises a one eighth (0.125) inchdiameter steel cable looped through at least one handle 1110 and aroundfluid conduit 1200, and retained in place by cable crimps 1120B, asshown in FIG. 10A. Generally, safety restraint 1120 operates as aredundant safety system that serves to prevent, or reduce, damage topersonnel or surrounding equipment and systems in the event collar 1106becomes disconnected, in an uncontrolled manner, from sleeve 1102.

With attention now to FIGS. 10 through 11C, details are providedconcerning various operational aspects of the illustrated embodiment. Assuch operational aspects are similar in many regard to those discussedelsewhere herein with respect to various alternative embodiments, thefollowing discussion will focus primarily on selected operationalaspects of the embodiment illustrated in FIGS. 10 through 11C.

In operation, the engagement of collar 1106 and sleeve 1102 is effectedby positioning each roller 1106A in a corresponding groove 1102C andcausing rollers 1106A to travel along grooves 1102C according to thepath denoted in FIG. 10B. More particularly, collar 1106 and sleeve 1102are brought together until each roller 1106A of collar 1106 ispositioned in the entry segment 1102D of a corresponding groove 1102C ofsleeve 1102. Rotation of collar 1106 is then initiated by way of handles1110. As a result of the angular orientation of entry segments 1102Dwith respect to a longitudinal axis BB defined by the cap assembly 1100,the initial rotation of collar 1106 causes collar 1106 to be drawntoward sleeve 1102, confining cap 1104 therebetween.

Continued rotation of collar 1106 causes rollers 1106A to complete theirtraverse of corresponding entry segments 1102D, and move into theirrespective intermediate segments 1102E. In at least some cases, rollers1106A travel to the respective ends of terminal intermediate 1102E. Inany event, rollers 1106A remain in intermediate segments 1102E untilsuch time as a predetermined pressure level is attained in a fluidpassageway 1300 (FIG. 10A) collectively defined by cap 1104 and fluidconduit 1200.

Subsequently, fluid is introduced into fluid passageway 1300, by way offluid conduit 1200 (FIG. 10A) connected with cap assembly 1100, therebypressurizing portion fluid passageway 1300. The pressure thus exerted,denoted at P₃ in FIG. 10A, transmits a force to cap 1104 which, in turn,transmits the force to collar 1106. Consequently, the exertion of P₃ inthis way forces rollers 1106A, attached to collar 1106, to lock up intocorresponding terminal segments 1102F of grooves 1102C and remaintherein, as indicated in FIG. 10A.

In the illustrated embodiment, the forward motion of collar 1106 may,depending on the position of rollers 1106A at the time of pressurizationof fluid passageway 1300, be accompanied by a rotary motion of collar1106 as well, as rollers 1106A travel along intermediate segments 1102Eand come to rest in terminal segment 1102F of groove 1102C. Generally,such rotary motion of collar 1106 is achieved in the substantially thesame way as the rotary motion of first housing portion 702, discussedabove.

Once rollers 1106A are seated in their corresponding terminal segments1102F of grooves 1102C, the continuing presence of pressure P₃ exerts aforce on cap 1104 that resists motion of rollers 1106A in the oppositedirection, that is, out of their corresponding terminal segments 1102F,and thereby aids in the retention of rollers 1106A in such terminalsegments. As a result, collar 1106 and sleeve 1102 of cap assembly 1100cannot be disengaged from each other until the fluid pressure in fluidpassageway 1300 has been reduced to a predetermined level ordifferential.

Thus, the rollers 1106A and grooves 1102C cooperate with each other, andadvantageously employ the line pressure, to ensure a secure connectionbetween collar 1106 and sleeve 1102 of cap assembly 1100 subsequent topressurization of fluid passageway 1300. Thus, the likelihood ofinadvertent, or intentional, removal of cap 1104 while a potentiallydangerous level of pressure exists in fluid passageway 1300, ismaterially reduced.

Directing attention now to FIG. 12, details are provided concerning analternative embodiment of a groove arrangement including a plurality ofgrooves generally denoted at 1400. Note that in the interest of clarity,the generally cylindrical structural element wherein the grooves 1400are formed is shown flat, rather than in a perspective view. Similar toother embodiments of grooves disclosed herein, groove 1400 includes aplurality of segments, including an entry segment 1400A. In contrastwith such other embodiments however, groove 1400 further includes fourintermediate segments denoted, respectively, 1400B, 1400C, 1400D and1400E as well as a terminal segment 1400F. Moreover, in embodiments ofthe invention employing configurations such as grooves 1400, the finalresting position of the associated rollers (not shown), that is, afterthe associated fluid passageway has been pressurized, is in terminalsegment 1400F, rather than in one of the intermediate segments 1400B and1400C.

Although in the exemplary embodiment illustrated in FIG. 12, grooves1400 are illustrated that include four intermediate segments, one ormore aspects of grooves 1400 may be varied as necessary to suit aparticular application. For example, intermediate segments 1400B, 1400Dand 1400F are, in some embodiments, generally parallel to each other. Inyet other embodiments, such intermediate segments are disposed in anon-parallel arrangement. The same is likewise true with respect tosegments 1400A, 1400C and 1400E. Moreover, other features such as, butnot limited to, the length, width and depth of one or more grooves 1400may be modified as required/desired.

It should thus be noted that the foregoing, and other, arrangements ofgrooves, as well as the type and arrangement of their associatedengagement members, disclosed herein are exemplary only and are notintended to limit the scope of the invention. By way of example, inanother exemplary embodiment (not shown), one or more of such groovessubstantially describes a “J” shape, such that line pressure causes thecorresponding engagement member to lock into a location proximate theend of the “hook” portion of the “J” shaped groove.

The described embodiments are to be considered in all respects only asexemplary and not restrictive. The scope of the invention is, therefore,indicated by the appended claims rather than by the foregoingdescription. All changes which come within the meaning and range ofequivalency of the claims are to be embraced within their scope.

1. A dry break valve assembly, comprising: (a) a first housing portion;(b) a first flow control assembly substantially disposed within saidfirst housing portion; (c) a collar attached to said first housingportion and including at least one engagement member; (d) a secondhousing portion configured to removably engage said collar, said secondhousing portion defining at least one groove extending at leastpartially about a circumference of said second housing portion, said atleast one groove being configured and arranged to advance said secondhousing portion toward said first housing portion by and while rotatingsaid second housing portion relative to said first housing portion andto receive said at least one engagement member and, when said first andsecond housing portions are engaged with each other so as to at leastpartially define a fluid passageway, said groove being configured andarranged so that said at least one engagement member is positionedtherein so as to be acted upon, at least indirectly, by a forceresulting from the presence of fluid pressure in said fluid passageway;(e) a second flow control assembly substantially disposed within saidsecond housing portion; and (f) an actuating mechanism substantiallydisposed within said fluid passageway for selectively opening andclosing said fluid passageway, said actuating mechanism comprising: acam mechanism adapted for selective rotation to open or close said fluidpassageway; a displacement shaft having a first end pivotally coupled toa first side of said cam mechanism and a second end coupled to saidfirst flow control assembly; and a drive shaft having a first endpivotally coupled to a second side of said cam mechanism and a secondend adapted to engage said second flow control assembly.
 2. The drybreak valve assembly as recited in claim 1, wherein said first andsecond flow control assemblies are operably connected with each otherwhen said first and second housing portions are engaged with each other.3. The dry break valve assembly as recited in claim 1, wherein saidactuating mechanism further comprises an actuating lever operablyconnected with said cam mechanism to facilitate selective rotation ofsaid cam mechanism.
 4. The dry break valve assembly as recited in claim1, wherein said actuating mechanism is substantially disposed withinsaid first housing portion.
 5. The dry break valve assembly as recitedin claim 1, wherein when said fluid pressure reaches a predeterminedvalue, said at least one engagement member is positioned in a terminalsegment of said at least one groove.
 6. The dry break valve assembly asrecited in claim 1, wherein said at least one groove has length formingan arc of about one hundred twenty degrees.
 7. The dry break valveassembly as recited in claim 1, wherein said at least one engagementmember comprises a pin.
 8. The dry break valve assembly as recited inclaim 1, wherein said at least one engagement member comprises threepins disposed in a spaced-apart arrangement about a circumference ofsaid collar, and wherein said at least one groove comprises threegrooves.
 9. The dry break valve assembly as recited in claim 1, whereinsaid at least one groove is substantially in the shape of a “J.”
 10. Thedry break valve assembly as recited in claim 1, wherein said at leastone groove has a substantially constant width, wherein said at least onegroove comprises a plurality of segments each having said substantiallyconstant width.
 11. A coupling for use in a pressurized fluid system,comprising: (a) a first coupling element having at least one roller onan internal surface thereof; (b) a second coupling element having: (i)an open first end, wherein said open first end is adapted to be receivedwithin said first coupling element; (ii) a groove formed in an externalsurface of said second coupling element and extending from said openfirst end along a length of said second coupling element, said groovehaving a length substantially greater than its width, said length ofsaid groove extending at least partially around a circumferentialsurface of said second coupling element in a manner such that when saidroller of said first coupling member is introduced into said groove atsaid open first end of said second coupling element, movement of saidroller along said length of said groove, and thus closer engagement ofsaid first coupling element to said second coupling element, requiresrotation of said first coupling element relative to said second couplingelement, and said groove having a substantially constant width, whereinsaid groove comprises a plurality of segments each having saidsubstantially constant width; and (c) an actuating mechanismsubstantially disposed within a fluid passageway formed by said firstand second coupling elements for selectively opening and closing saidfluid passageway, said actuating mechanism comprising: a cam mechanismadapted for selective rotation to open or close said fluid passageway; adisplacement shaft having a first end pivotally coupled to a first sideof said cam mechanism and a second end coupled to a first flow controlassembly; and a drive shaft having a first end pivotally coupled to asecond side of said cam mechanism and a second end adapted to engage asecond flow control assembly.
 12. The coupling as recited in claim 11,further comprising a valve assembly disposed within at least one of saidfirst coupling element and said second coupling element.
 13. Thecoupling as recited in claim 11, wherein said second coupling elementhas an end surface at said first open end, and wherein said groovestarts at said end surface and extends at least partially around saidcircumferential surface of said second housing portion at an acute anglefrom said end surface.
 14. The coupling as recited in claim 13, whereinsaid groove includes: (a) an entry segment starting at said end segment,said entry segment extending at an acute angle from said end surface;(b) an intermediate segment disposed at an interior end of the entrysegment; and (c) a terminal segment offset from said intermediatesegment at an acute angle.
 15. The coupling as recited in claim 14,wherein said coupling is configured such that when line pressure ispresent in a fluid passageway defined by said first and second couplingelements, said line pressure forces said engagement member from saidintermediate segment into said terminal segment, thereby causing saidfirst coupling element to rotate relative to said second couplingelement and to lock said roller within said terminal segment while saidline pressure is present.
 16. The coupling as recited in claim 14,wherein said groove has a substantially constant width, and wherein eachof said entry segment, intermediate segment, and said terminal segmentare substantially linear and have said substantially constant width.